Turbotransmission



Nov. 28; 1944. R. J. MILLER TURBO TRANSMISSION Filed April 28. 1941 2 Sheets-Sheet 2 A INWYNTOR` /A VMM@ J M/LER Patented Nov. 28, 1944 TURBOTRANSMISSION Raymond J. Miller, Detroit, Mich., assigner to Hydraulic Brake Company. Detroit. Mich., a corporation of California Application April 28, 1941, Serial No. 390,810

6 Claims.

'Ihis invention relates to transmissions, and more particularly to fluid transmissions for motor vehicles.

The invention contemplates a fluid transmission including an impeller, a turbine driven' thereby, and means for eifectively reducing frictional resistance between the impeller and the turbine when great diiferential in the speed of the impeller and turbine occurs.

An object of the invention is to provide a fluid transmission including an impeller, a turbine driven by the impeller, and a differential pump operative to automatically deliver a large volume of uid to the unit when the turbine is substantially static so as to disperse heat and also to reduce frictional resistance between the impeller and the turbine.

Another object of the invention is to provide a fluid transmission for a motor vehicle including an impeller, a turbine driven thereby, and a differential pump for delivery of varying volumes of fluid to the impeller, the rotor of the pump having reversed direction of rotation from that of the impeller and turbine.

Other objects and advantages of the invention will appear from the following description taken in connection with the drawings forming a part of this specicationii and in whichl Fig. 1 is a vertical sectional view of a fluid torque converter embodying the invention;

Fig. 2 is a sectional view substantially on line 2-2, Fig. 1;

Fig. 3 is a sectional view substantially on line 3-3, Fig. 1; and A f Fig. 4 is a fragmentary view of the feed screw. Referring to the drawings for more specific details of the invention, I0 represents the crank case of an internal combustion engine, and I2 the crank shaft of the engine. The crank case I0 has secured thereto a bell housing I4 enclosing a reservoir I6 provided with a filling opening I8, in the wall of the bell housing, normally closed by a plug 20.

'Ifhereservoir is preferably annular, and on its inner perimeter is a hollow flange 22 communieating with the reservoir. A tube 24 formed integral with the perimeter of the flange 22 extends upwardly therefrom, and an inlet port 26 in the perimeter of the flange communicates with the tube, and, correspondingly, a tube 28 formed integral with the perimeter of the flange 22 extends downwardly therefrom, and an outlet port 30 in the perimeter of the flange communicates with the tube 28.

Air ducts 32 are arranged in parallel relation 55 to one another on each side of the tube 24, and a diaphragm 34, providing a sump 36 has an opening 38 communicating with the tube 28, and also a plurality of apertures 40 providing communications between the reservoir and the sump. l

Heated fluid enters through the intake port 26, passes upwardly through the tube 24, thence spreads and passes downwardly betweenv the air ducts 32, where it is cooled, into that portion of the reservoir below the air ducts, thence through the apertures 40 in the diaphragm into the sump 36, `from where it is drawn through the tube 28 and outlet port 30 by pumping means, to be hereinafter described.

A ring 42 secured to one side of the flange 22 supports a fluid seal 44, and a pair of oppositely disposed rings 46 and 48 are secured to the other side of the fiange 22. The ring 46 has an opening 50 therethrough registering with the outlet port 30 of the reservoir, and this ring also has internal splines 52, and the ring 48 supports a bearing 54 and a fluid seal 56.

A iiuid torque converter, indicated generally at 58, includes a housing having a hub 62 suitably secured to the crank shaft I2, and a hub 64 in oppositely disposed relation to the hub 62 embraced by the uid seal 44. The hub 62 has a concentric bore, and fitted in this bore is a bearing 66. s the housing 60" for connecting a starter, not shown, and mounted on the inner wall of the housing is a shroud 'I0 having arranged thereon a plurality of impeller blades 12 supporting an inner shroud 14.

A center shaft 16 mounted for rotation on the bearings 54 and 66 in axial alignment with the crank shaft I2, has splined thereto a clutch member 18and the hub of this clutch member is embraced by the uid seal 56 for inhibiting seepage of uid from the housing 60. The center shaft 16 has in one end thereof a concentric bore, and fitted in this bore is a bearing supporting a driven shaft 82,`and the driven shaft carries a clutch member, not shown, for cooperation with the clutch member 18, and a difierential fluid pump 84 is mounted on the otherhas an inlet port 90 and a discharge port 92; the

latter communicating with the housing 60 of the torque converter. A needle bearing 94 on the A ring gear 68 is suitably mounted on hub of the housing 86 supports a rotor 96 having a plurality of blades 98 in wiping engagement with the wall of the pump chamber. The blades may be of any preferred type. The rotor also has a flange provided with a beveled face |02 oppositely disposed and in concentric relation to a circumferential beveled face |04 on the hub 62, and a plurality of spaced spring-pressed plungers |06 rotatably carried by the housing 86 of the pump have conical heads |08 cooperating with the beveled faces |02 and |04 to yieldingly couple the rotor 96 of the pump to the hub of the impeller.

A turbine associated with the impeller includes a web ||0 supported on and flxedly secured to the pump housing for rotation therewith. The web supports a two-stage turbine ||2 and ||4 within the housing 60 in oppositely disposed relation to the impeller and provides in conjunction therewith a fluid circuit. iAs shown, the two-stage turbine includes an outer shroud section ||6 having secured thereto a plurality of vanes I8 constituting the first stage of the turbine. I'he vanes ||8 support an inner shroud section |20, flxedly secured to another inner shroud section |22 adjacent the inner shroud section 14, and the inner shroud section |22 is fixedly secured to an inner shroud section |24 supported on a plurality of vanes |26 fixedly secured to an outer shroud section |28 mounted on the web ||0 and constituting the second stage of the turbine.

A sleeve |29 slipped over the center shaft 16 has on one end external splines received by the splines 52 on the ring 46, and the sleeve is supported by the ring |46 in spaced relation to the center shaft to provide in conjunction therewith an annular channel |30, constituting a communication between the outlet port 30 of the reservoir and the inlet port 90 of the pump.

Fluid is discharged from the pump into the housing 60, passes through the fluid circuit, where it becomes heated, :thence from the houslng, through the hub 64, and intake port 26, into the reservoir. The other end of the sleeve |29 has a reduced portion |32, and fitted on this reduced portion is a heavy sleeve |34 and a ring |36. The sleeve |34 and ring |36 are fixedly secured to one another and also to the sleeve |29. The sleeve |34 has external threads |38 provided with rounded approaches |40. A needle bearing |42 on the sleeve |29 supports for slight rotation the reaction member are springs |18 of varied lengths for progressively resisting movement of lthe reaction member tending to move the vanes |86 into the fluid circuit.

In a normal operation, assuming that the unit is filled with fluid to its normal capacity, transmission of force from the power plant to the crank shaft resultsin driving the impeller and the pump. The housing 86 of the pump is keyed to the center shaft 16 and the rotor 98 of the pump is journaled in the chamber 88. The rotor has conventional spring-pressed blades 98 in wiping engagement with the wall of the chamber, and a flange |00 having a beveled face |02 concentrically disposed with relation to the beveled face |04 on the hub 62 secured to the crankshaft |2, while spring-pressed plungers |06 rotatably mounted on the housing have conical heads |08 interposed between the beveled faces |02 and |04. 'I'his provides for driving the rotor of the pump in reverse direction of rotation from that of the impeller and the center shaft supporting the pump housing, resulting in frictional resistance proportionate to the differential in speed of rotation of the driving shaft I2 and the center shaft 16. The pump draws fluid from the reservoir through the outlet port 30, the pasa sleeve |44 having a peripheral flange |46 provided with threads |48 0f the same Ditch as the threads |38, and the approach ends of the threads |48 have dogs |50. A collar |52 is suitably secured on the sleeve |29 and a brake |54 interposed between fthe collar and the sleeve |44 yieldingly resists movement of the sleeve in both directions of rotation.

A carrier |56 adapted to travel on the sleeves |34 and |44 has internal threads |58 for cooperation with the threads |38 and |48 on the sleeves |34 and |44, respectively. The carrier has suitably secured thereto a sleeve |60 supporting a reaction member |62 including a web |64 having thereon a plurality of vanes |66 adapted to move into and out of the fluid circuit between the first and second stages of the turbine, and the vanes |66 support a shroud |68 having thereon a. plurality of index vanes |10 supporting a shroud |12.

A ring |14 supported on the ring |36 has thereon spaced rods |16 extended through openings in the web |64 of the reaction member, and sleeved on these rods between the ring |14 and sage 50, the annular channel |80, through the inlet port into the chamber 88, and discharges the fluid through the outlet 92 into the vortex chamber. The fluid is delivered to the impeller by the pump at a rate proportionate to the speed of rotation of the crank shaft. The impeller energizes the fluid, and the energy of the fluid is received on the vanes constituting the ilrst stage ||2 of the turbine, and on the vanes |66 of the reaction member |62, causing rotation of the turbine.

This rotation of the turbine results in driving the center shaft 16 and the driven shaft 82 clutched thereto. Upon rotation of the center shaft, the housing 88 of the pump is driven, and, accordingly, a smaller volume of fluid is delivered to the impeller because the differential in speed of the impeller and turbine now becomes less.

As the speed of rotation of the impeller increases, the energy of the fluid increases proportionately, and this increased energy of the fluid acting on the vanes ||8'of the turbine causes increase in speed of the turbine. As this increased speed approaches that of the impeller, the angle of the fluid leaving the rst stage of the turbine shifts from impingng on the faces of the reaction vanes |66 tol impinge upon the backs of the vanes, causing the reaction member |62 to spiral on the threaded sleeve |34 out of the fluid circuit onto the sleeve |44, and as' the reaction membei retracts, the index vanes |10 carried thereby move in between the first and second stages of the turbine and direct the flow of fluid from the first stage ||2 of the turbine to the second stage ||4 thereof, and under this condition the transmission functions as a fluid coupling.

Upon decrease in difference of the speed of rotation of the impeller and the turbine, the volume of fluid delivered by the pump decreases proportionately. As an increased load is imposed on the turbine, the differential in speed increases, and the pump delivers an increased volume of fluid. Concomitantly therewith, the angle of discharge from the first stage of the turbine shifts because of demand of torque ratio, and impinges on the face of the index vanes |10, causing the reaction member to spiral into the fluid circuit.

Upon initial movement of the reaction memasoaoss y |40 serve to guide the threads |58 into engagement with the threads |38, and as the carrier advancesl on the threads |38 the reaction member |82 spirals into the fluid circuit against the progressively increasing resistance imposed by the springs |18.

' It is obvious from the foregoing that the pump delivers fluid to the impeller at a rate proportionate to the speed diivlerental between the impeller and the turbine, and thatA the maximum volume of iluid is delivered to the impeller when the turbine and the impeller are rotating at maximum differential speed, and, correspondingly, the minimum volume of uid is delivered by the pump to the impeller when Vthe turbine approaches the speed of the impeller. It is also obvious that the rotor of the pump rotates in reverse direction to that of the impeller and turbine, and, accordingly, imposes frictional resistance on the turbine proportionate to the differential in speed of rotation ofl the impeller and the turbine.

While this invention has been described in connection with certain speciiic embodiments, the principle involved is susceptible of numerous other applications that will readily occur to persons skilled in the art. The invention is, therefore, to be limited only as indicated bythe scope of the appended claims.

Having thus described the various features of the invention, what I claim as new and desire to secure by Letters Patent is:

l. A iluid transmission comprising an impeller. a, turbine providing in conjunction therewith a iiuid circuit, and a` pump for delivery of fluid into the circuit including a rotor arranged coaxially withrelation to the impeller and turbine and rotative in oppositedirection from that of the impeller and turbine and a housing for the rotor carried by the turbine.

2. A uid transmission comprising an impeller, a turbine providing in conjunction therewith a fluid circuit, and a pump having a rotor and a housing connected respectively to the impeller and turbine for delivery of iiuid into the circuit at a rate decreasing as the diil'erenti'al in speed of rotation of the impeller and turbine decreases, the rotor and housing operative in reverse directions of rotation.

3. A fluid. transmission comprising an impeller,v

a turbine providing in conjunction therewith a fluid circuit, and a pump having a rotor and a housing connected respectively to the impeller and the turbine for delivery of fluid into the circuit in volume decreasing proportionately to the decreased differential speed of rotation of the impeller in relation to the turbine, the rotor rotative in reverse direction to that oi' the housing so as to oppose the resistance presented by the turbine.

4. .A iiuid transmission comprising an impeller, a turbine providing in conjunction therewith a vortex chamber, a pump for delivery of iiuld intoV the chamber having a housing fixedly secured to the turbine, and means connecting the rotor of the pump to the impeller to provide for reverse rotation between the rotor'and the housing.

5. A iiuid transmission comprising a primary means for energizing fluid and secondary means for receiving energy from the fluid providing in conjunction with one another a fluid power transmitting circuit, means for deliveryt of fluid into the circuit, an element of the delivery means connected to the secondary means and means .connected tothe secondary means for coupling another element of the delivery means to the primary means whereby the respective elements of the delivery means rotate reversely to one another so as to oppose resistance presented by the secondary means.

6. A uid transmission comprising a primary means for energizing iluid and a secondary means receiving energy from the iiuid providing in conjunction with one another a fluid power transmission circuit, and a rotary pump for delivery of iluid into the circuit having its rotor driven from the primary means in reverse direction to rotation of the primary means and its housing l means.

carried by the secondary means and functioning to change resistance to movement of the secondary means in proportion to the diil'erential in speed of rotation of the primary and secondary RAYMOND J. MIILER. 

